Torque transmission device for motor vehicle

ABSTRACT

A torsional damping device (110) includes a movable torque input element (130, 140), a movable torque output element (150), at least one phasing member (320,340) and at least one group of elastic members (250, 260) mounted between the torque input element and torque output element. The at least one group of elastic members acts against rotation of the torque input element and the torque output element with respect to one another. The elastic members of the at least one group of elastic members are arranged in series by the at least one phasing member (320, 340) so that the elastic members of the at least one group of elastic members deform in phase with one another. The torque input element having at least one stop member (620) limiting rotation of the torque input elememt relative to the output element and relative to the at least one phasing member.

CROSS-REFERENCE TO RELATED APPLICATIONS AND CLAIM TO PRIORITY

This application is related to Patent Application No. 1557109 filed Jul.24, 2015 in France, the disclosure of which is incorporated herein byreference and to which priority is claimed.

FIELD OF THE INVENTION

The present invention relates to a torsional damping device, inparticular for a motor vehicle transmission system.

BACKGROUND OF THE INVENTION

In such an application the torsional damping device can be integratedinto a torsional damping system of a clutch capable of selectivelyconnecting the combustion engine to the gearbox, in order to filtervibrations due to irregularities of the engine.

As a variant, in such an application the torsional damping device can beintegrated into a dual mass flywheel, into a friction disk of theclutch, or into a hydrodynamic torque converter.

The invention also relates to a transmission assemblage for a motorvehicle of the hybrid type, in which an electric machine is disposed inthe transmission system between the engine and the gearbox.

A device of this kind has, in general, a torque input element, a torqueoutput element, and elastic members mounted between the torque inputelement and torque output element and acting against rotation of thetorque input element and torque output element with respect to oneanother.

When the torque transmission device is of the “long travel damper” (LTD)type, it comprises several groups of elastic members, the elasticmembers of a given group being arranged in series by means of a phasingmember so that the elastic members of each group deform in phase withone another.

When the elastic members are helical compression springs, excessivecompression of those spring can bring the turns into contact with oneanother. The turns are then referred to as “contiguous.” If the torquebeing transmitted is large, the turns experience crushing which causesfatigue and premature wear on the springs.

It is necessary in general to be able to limit the angular deflectionsamong all the movable elements of the torque transmission device, whichis not achieved in the existing art.

The document U.S. Pat. No. 8,047,922 discloses a torsional damper havingtorque input elements and torque output elements between which arearranged several groups of elastic members arranged in series by meansof a phasing member. Stops are provided between the torque input elementon the one hand and the phasing member or the annular web on the otherhand.

A damper of this kind has a relatively complex structure and does notallow the aforesaid problems of deflection control and/or spring damageto be solved.

SUMMARY OF THE INVENTION

An object of the invention is in particular to provide a simple,effective, and economical solution to this problem.

The invention proposes for this purpose a torsional damping devicehaving a movable torque input element, a movable torque output element,and at least one group of elastic members mounted between the torqueinput element and torque output element and acting against rotation ofthe torque input element and torque output element with respect to oneanother, the elastic members of this group being arranged in series bymeans of at least one phasing member in such a way that the elasticmembers of each group deform in phase with one another, the torque inputelement having at least one stop means limiting its relative rotationwith respect to the output element and with respect to the phasingmember.

In an embodiment of the invention, the torque input element isconstituted by a first guide washer and by a second guide washer, saidguide washers being connected to one another by at least one firstconnecting means, the connecting means constituting the first stopmeans.

In an embodiment of the invention, the stop means constitutes aconnecting spacer.

In an embodiment of the invention, the stop means traverses the phasingmember.

In an embodiment of the invention, the phasing member has at least oneoblong receptacle, the stop means traversing the phasing member throughthe oblong receptacle.

In an embodiment of the invention, the stop means has a cylindricalshape of circular, oval, or prismatic cross section.

In an embodiment of the invention, the phasing member is constituted bya first phase washer and by a second phase washer, the two phase washersbeing connected to one another by at least one second connecting meansand being placed on either side of the torque input element or of thetorque output element.

In an embodiment of the invention, the phasing member is constituted bya first phase washer and by a second phase washer, the two phase washersbeing connected to one another by at least one second connecting means,the second connecting means being located on the same circle as the oneon which the stop means is disposed.

In an embodiment of the invention, the torque output element isconstituted by a web, the first phase washer and the second phase washerbeing placed on either side of the web, the stop means extending betweenthe first guide washer and the second guide washer while traversing thefirst guide washer, the web, and the second guide washer.

Also an object of the invention is a component for a transmission systemof a motor vehicle, the component being in particular a dual massflywheel, a hydrodynamic torque converter, or a friction disk,comprising a damping device as described above.

A final object of the invention is a motor vehicle transmissionassemblage, intended to be disposed between a combustion engine equippedwith a crankshaft and a gearbox equipped with an input shaft, saidassemblage comprising:

-   -   an electric machine having a stator and a rotor rotationally        movable around an axis X;    -   a clutch arranged to rotationally couple or decouple the        crankshaft of the engine and the rotor;    -   a torsional damping device as described above, the damping        device being arranged to transmit a torque and to damp        rotational irregularities between the rotor and the input shaft        of the gearbox.

BRIEF DESCRIPTION OF THE DRAWINGS

The invention will be better understood, and other details,characteristics, and advantages of the invention will emerge, uponreading the description below provided as a non-limiting example withreference to the attached drawings, in which:

FIG. 1 is a diagram of a transmission assemblage according to a firstembodiment of the invention;

FIG. 2 is an axial half section view of a friction clutch comprising atorsional damping device, according to an embodiment of the invention;

FIGS. 3a and 3b are three-dimensional depictions of the damping devicerespectively from a first side of said device and from a second side ofsaid device, according to an embodiment of the invention;

FIGS. 4a and 4b are schematic depictions of the web and of the phasingmember at a stop respectively in the forward direction (D) and in thereverse direction (R).

FIG. 5 is a perspective depiction of a web of a torsional damping deviceaccording to an embodiment of the invention;

FIG. 6 is a perspective depiction of a first face of the phasing memberaccording to an embodiment of the invention;

FIG. 7 is a perspective depiction of a second face of the phasing memberaccording to the same embodiment as that of FIG. 6;

FIG. 8a is a schematic depiction of the damping device according to anembodiment of the invention;

FIGS. 8b and 8c are cross sections of the damping device along an axis Aand an axis B of FIG. 8 a;

FIG. 9 is a depiction of a damping device comprising a stop element,according to an embodiment of the invention;

FIG. 10 is a perspective view of the damping device according to FIG. 9,according to an embodiment of the invention;

FIG. 11 is a depiction of a transmission assemblage according to anembodiment of the invention;

FIG. 12 is a depiction of a damping device according to an embodiment ofthe invention;

FIG. 13 is a depiction of a damping device according to a variant of theinvention;

FIG. 14 is a partial section view of a damping device according to avariant of the invention;

FIG. 15 is a section view illustrating a damping device according to thevariant illustrated in FIG. 14; and

FIG. 16 is a partial section view of a damping device according to anembodiment of the invention.

In the description and the claims the terms “outer” and “inner,” as wellas the orientations “axial” and “radial,” will be used to designateelements of a transmission assemblage in accordance with the definitionsgiven in the description. By convention, the “radial” orientation isdirected orthogonally to the rotation axis X of the transmissionassemblage which determines the “axial” orientation, and from inside tooutside moving away from said axis. The terms “outer” and “inner” areused to define the relative position of one element with respect toanother with reference to the axis X; an element close to the axis isthus referred to as “inner” as opposed to an “outer” element locatedradially at the periphery. The terms “rear” (AR) and “front” (AV) arefurthermore used to define the relative position of one element withrespect to another and with respect to the direction in which thevehicle proceeds when the vehicle is driving forward.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT(S)

FIG. 1 illustrates a transmission assemblage disposed between acombustion engine 1 and a gearbox 2, according to an embodiment of theinvention. The transmission assemblage has a first friction clutch 330,a torsional damping device 4, an electric machine 500 comprising astator 501 and a rotor 502, and a second friction clutch 332.

FIG. 2 illustrates first friction clutch 330 associated with torsionaldamping device 4. First friction clutch 330 is connected to an inertialwheel 3. Inertial wheel 3 has a first annular region 6 extendingradially, and a cylindrical region 7 extending axially toward to therear from the outer periphery of first annular region 6. A secondcylindrical region 8 and an annular cover 9 are fastened on cylindricalregion 7. First annular region 6, cylindrical region 7, and secondannular region 8 define an annular chamber 10.

Inertial wheel 3 also has orifices (not depicted) configured in firstannular region 6. Fastening screws (not depicted), engaged into theorifices, allow inertial wheel 3 to be fastened to the end of thecrankshaft.

Friction clutch 330 has a reaction plate constituted by second annularregion 8, a pressure plate 11, and a friction disk 12. Pressure plate 11is axially movable in order to be brought into contact with frictiondisk 12 upon transmission of torque between the combustion engine andthe input shaft of the gearbox. An annular actuation element ordiaphragm 96 axially loads pressure plate 11 against friction disk 12and reaction plate 8.

In a variant that is not depicted, the clutch can be of the normallyopen type. In this case it is the rearward motion of a release bearing(not depicted) that allows pressure plate 11 to be loaded, via diaphragm96, toward reaction plate 8. In a normally open clutch of this kind,diaphragm 96 exhibits appropriate elasticity for returning its fingersto a front, inactive position.

Torsional damper 4 comprises a rear guide washer 13 remote from engine 1and a front guide washer 14 close to engine 1. Torsional damping device4 also has a web 15 and a splined hub 16, in this example constitutingan integral assemblage. As a variant, web 15 and splined hub 16 couldconstitute two distinct parts and could be fastened to one another bymeans of rivets or a weld. Splined hub 16 is intended to interact withsplines of complementary shape carried by the rear end (not depicted) ofthe input shaft of gearbox 2.

Rear guide washer 13 and front guide washer 14 are disposed axially oneither side of web 15. Rear guide washer 13 is fastened to friction disk12 by means of fastening members such as screws or rivets (notdepicted). Rear guide washer 13 has at least one hole 107. In anexample, rear guide washer 13 has six holes such as 107, distributedcircumferentially.

Rear guide washer 13 and front guide washer 14 are furthermore centeredand rotationally guided on splined hub 16 respectively by means of arear bearing 17 and a front bearing 18. Bearings 17 and 18 can eachconstitute a plain bearing or rolling bearing.

Bearings 17 and 18 each have an L-shape. Rear bearing 17 and frontbearing 18 are disposed in abutment against a radial portion 101 of hub16. Central hub 16 also has a cylindrical portion 102 from which radialportion 101 extends. Cylindrical portion 102 has on an inner periphery atooth set complementary to that of the rear end of the input shaft ofgearbox 2.

Rear 13 guide washer and front guide washer 14 each have a respectiveinner rim 19 and 20 defining an abutment surface for the correspondingbearing. Bearings 17 and 18 furthermore each have a respective radiallyinner face 21 and 22 that interacts with a respective annular outersurface 23 and 24 of splined hub 16 for rotational driving of bearings17 and 18 by hub 16. Front bearing 18 constitutes an axial protrusion 99extending toward the front.

At least one of bearings 17 or 18 could be replaced by a tapered bearing105 as illustrated in FIG. 16. This results in a tapered abutmentagainst hub 16 in order to absorb any alignment errors of the inputshaft of the gearbox and of the output shaft of the motor.

Torsional damping device 4 furthermore has a plurality of groups of twoelastic members 25, 26 ensuring coupling between the two guide washers13, 14 and web 15. Elastic members 25, 26 here are straight elasticmembers distributed circumferentially along the same circle around axisX. The springs could be curved.

Each elastic member can have two coaxial springs mounted one insideanother. In the embodiment depicted, torsional damping device 4 hasthree groups of two straight elastic springs.

In FIGS. 3a and 3b the elastic members are received in a receivingchamber defined by indented annular regions such as 27 and 270,configured in the respective guide washers 13 and 14 and extendingcircumferentially.

In addition, each group of elastic members extends circumferentially, onthe one hand between two abutment seats (not depicted) carried by guidewashers 13 and 14, and on the other hand between two circumferentiallyconsecutive abutment tabs 59, 60 of web 15.

Specifically, in FIG. 4 web 15 has three abutment tabs 59, 60, and 61.Each of them has two substantially planar abutment faces 62, 63 servingfor abutment of the ends of elastic members 25, 26. Tabs 59, 60, 61 ofweb 15 can furthermore have retaining pins (not depicted) that extendcircumferentially on either side of the tabs and allow radial retentionof the ends of elastic members 25, 26.

Web 15 is mounted rotationally fixedly on splined hub 16. Web 15 has aradially inner portion 64 and a radially outer portion 65, connected toone another by abutment tabs 59, 60, 61. Radially outer portion 65constitutes a ring. Note that radially inner portion 64 of web 15 isindistinguishable from radial portion 101 of hub 16. Abutment tabs 59,60, 61 extend to constitute an angular section that widens in proximityto radially outer portion 65.

Radially inner portion 64 and radially outer portion 65 delimit,radially between two circumferentially successive abutment tabs, awindow 70 for accommodating two elastic members 25, 26 of a given groupof elastic members.

In an example that is not illustrated, tabs 59, 60, and 61 of web 15 canalso have, on their radially outer end, projecting elements configuredto interact at a travel limit with stop surfaces carried by at least oneof guide washers 13, 14. The angular travel of the guide washers withrespect to web 15 is thus limited in order to protect the elasticmembers.

In FIG. 2 the elastic members of each group are mounted in series bymeans of at least one phasing member 32, 33. In the example according tothe invention, the phasing member is constituted by two phase washers, arear phase washer 32 and a front phase washer 33. The two phase washers32, 33 are mounted freely (i.e. without hindrance) rotatably withrespect to guide washers 13, 14 on the one hand, and with respect to web15 on the other hand. The two phase washers 32, 33 are disposed oneither side of web 15. The two phase washers 32 and 33 are coaxial.

Phase washers 32, 33 are each spaced axially away from second web 15 bya minimum operating clearance, for example 0.1 to 1 mm.

Phase washers 32, 33 are centered and rotationally guided on splined hub16 by web 15. To achieve this, rear phase washer 32 and front phasewasher 33 respectively have on their inner periphery a front lateralface 34 and a rear lateral face 35 intended respectively to end upfacing, or in fact to come into contact with, a rear lateral face 36 anda front lateral face 37 of web 15, at a location where inner annularportion 64 of web 15 is located. Note that axial protrusion 99 ofbearing 18 serves as an axial abutment face for front phase washer 33.

In FIGS. 2 and 6, phase washers 32, 33 are moreover connected to oneanother by at least one connecting means 57. The two phase washers 32,33 are each constituted by a metal sheet. Rear phase washer 32 has, atthe location where the connection of the two phase washers 32, 33 to oneanother is made, an indented shape 58 allowing the two phase washers 32,33 to move locally closer to one another. This proximity ensures axialand radial retention between phase washers 32, 33, and also with respectto web 15.

In the example according to an embodiment of the invention, it is rearphase washer 32 that has indentation 58, but it could be constitutedonly by front phase washer 33 or also by both phase washers 32, 33.

In the example, front phase washer 33 is planar.

In FIG. 6 each of the phase washers has radial phasing tabs such as 28,29, 42, which are each intercalated between a first elastic member 25and a second elastic member 26 so that the two consecutive elasticmembers 25, 26 of a given group are arranged in series. Radial phasingtabs 28, 29, 42 have two substantially planar abutment faces 73, 74 thatform an angle between them and serve for abutment of the ends of elasticmembers 25, 26. Each radial phasing tab can furthermore have, at itsradially outer edge, two opposite outer retaining pins (not depicted),which extend on either side of each radial phasing tab and allow theends of the elastic members to be radially and axially retained.

Phasing member 32, 33 is such that a deformation of the elastic membersin phase with one another is ensured, so that the elastic forcesgenerated in torsional damping device 4 are circumferentiallydistributed in homogeneous fashion.

Each group thus has, during operation, a first elastic member 25abutting at a first end against an abutment seat carried by guidewashers 13, 14 and at a second end against a radial phasing tab 28, 29,42 of phasing member 32, 33, while second elastic member 26 abuts at afirst end against said radial phasing tab 28, 29, 42 of phasing member32, 33 and at a second end against an abutment tab 59, 60, 61 of web 15.A driving torque is thus transmitted from guide washers 13, 14 to web 15by means of elastic members 25, 26.

Each of the phase washers, rear 32 and front 33, has a radially outerregion 38, 39 spaced away from one another (FIG. 6).

Each of the phase washers, rear 32 and front 33, has a radially innerregion 40, 41 spaced away from one another (FIG. 6).

Phasing tabs 28, 29, 42 extend radially from radially inner region 40,41 of each of the phase washers 32, 33 toward radially outer region 38,39, having a proximal end 43 close to radially inner region 40, 41 whichis narrower than a distal end 44 remote from radially inner region 40,41. Phasing tabs 28, 29, 42 extend in the form of an angular sector.

Indentation 58 is implemented at these phasing tabs, preferably at alocation close to radially outer region 38, 39.

Delimited circumferentially between two phasing tabs, and between theradially inner region and the radially outer region, is a window 71allowing the reception of two elastic members or springs 25, 26. In theexample illustrated in FIG. 6, spring 25 has a length, measuredcircumferentially, that is less than the length of second spring 26. Theopposite case is also conceivable, however, with the length of spring 25being greater than that of second spring 26 (example not illustrated).

Web 15 and phase washers 32, 33 have the same radius. Neither web 15,nor phase washers 32, 33, go beyond one another. The damping deviceaccording to the invention is thus, advantageously, radially compact.

In the embodiment depicted in FIGS. 5 and 7, web 15 has at least onerear axial stud 66 and at least one front axial stud 67. Each of thesestuds 66, 67 constitutes a protrusion that extends axially with respectto rotation axis X of damping device 4 and with respect to the plane inwhich web 15 extends.

Rear phase washer 32 and front phase washer 33 also each have at leastone receptacle 68, 69 constituted through each of the phase washers(FIGS. 5 and 7). The receptacle is preferably oblong in shape.

Axial stud 66, 67 and the corresponding receptacle 68, 69 are arrangedwith respect to one another in such a way that the axial stud becomesinserted through the receptacle. The axial studs constitute stop meansthat limit the relative rotation of web 15 and of front and rear phasewashers 32, 33 in two opposite rotation directions, i.e. in the forwarddirection (D) (FIG. 4a ) or reverse direction (R) (FIG. 4b ).

Axial stud 66, 67 is situated circumferentially between two tabs of theweb. More specifically, axial stud 66, 67 is situated radially betweensplined hub 16 and window 71 that receives two elastic members 25, 26,and axially between radially inner portion 64 and tab 59, 60, 61.

Rear phase washer 32 and front phase washer 33 each respectively havethree receptacles such as 68 and 69, each intended to receive arespective stud such as 66 and 67. Each of the studs is intended to comeinto abutment against an edge of receptacle 68, 69.

Stud 66, 67 can be constituted by a peg distinct from web 15 (examplenot depicted) which is inserted through web 15 by press-fitting, orfastened by welding or riveting. The peg can then be designed so that atleast one end of said peg projects from web 15. As a variant, the pegprojects from both sides of web 15.

In FIGS. 5, 7, 8 a, 8 b, 8 c the stud is implemented by materialextrusion. In the example of the invention, stud 66 is intended tointeract with rear phase washer 32, and stud 67 is intended to interactwith front phase washer 33. Studs 66 and 67 are each constituted on thesame circle. FIG. 8a illustrates the damping device, and FIGS. 8b and 8crespectively illustrate sections of the damping device along a firstsection A and along a second section B passing respectively through stud66 and through the two studs 66 and 67.

In a variant that is not illustrated, the two studs 66 and 67 could beradially aligned.

Rear phase washer 32 and front phase washer 33 are also connected to oneanother by means of a connecting member 52 constituting a connectingspacer 52.

According to an embodiment of the invention, connecting spacer 52 isdisposed on the same circle as the one on which studs 66, 67 areconstituted.

In FIG. 2, damping device 4 also has a pendulum damper 48 comprising asupport member 49 and a plurality of pendulum flyweights 50 distributedcircumferentially on support member 49. Support member 49 of pendulumdamper 48 constitutes a disk which has a first portion that extendsradially and a second portion that extends axially. The second portionis intended to come into abutment against bearing 18. In the example,the second portion of support member 49 extends toward the front.

Support member 49 has receiving orifices 51 that allow the passage ofconnecting member 52, such as rivets, allowing support member 49 to beintegrated with rear phase washer 32 and front phase washer 33. Thefastening of support member 49 to rear phase washer 32 and front phasewasher 33 is implemented through an orifice 53 constituted through frontguide washer 14. According to an embodiment of the invention, orifice 53is oblong in shape and extends circumferentially over a length definedso that connecting member 52 does not come into contact with an edge ofsaid orifice 53, regardless of the operating conditions of thetransmission assemblage. Hole 107 constituted through rear guide washer13 thus serves for phasing of that connecting member 52 upon assembly ofdevice 4.

Connecting member 52 thus connects the two phase washers 32, 33 to oneanother, and connects pendulum damper 48 to the two phase washers 32,33. In an embodiment of the invention, connecting member 52 is fastenedby riveting onto the support member of pendulum 49.

In the example, receptacles 68 and 69 and orifices 51 and 53 extendalong a circle of the same radius.

Fastening member 52 also constitutes a spacer between phase washers 32,33 and support member 49.

In addition, support member 49 is offset axially toward the front andextends between front guide washer 14 and inertial wheel 3. Pendulumflyweights 50 are mounted at an outer end of support member 49. In theexample of FIG. 2, pendulum flyweights 50 are installed radially outsidethe elastic members. Pendulum flyweights 50 can thus be installed at arelatively long radial distance from axis X, the result being to achieveoptimum filtering performance for pendulum oscillator 48.

Flyweights 50 are capable of oscillating with respect to support member49 in a plane orthogonal to rotation axis X in reaction to rotationalinconsistencies. Each flyweight 50 has two flanks 54, 55 that extendaxially on either side of support member 49 and are connected axially toone another by means of two connecting spacers such as 56. The operationof such flyweights is well known per se and will not be describedfurther here. Other architectures for pendulum damper 48 are alsoconceivable.

Receptacles 68 and 69, constituted respectively through rear phasewasher 32 and through front phase washer 33, are located on the samecircle as the one along which orifice 53 is constituted. In anembodiment of the invention, orifice 53 extends along a circular arclarger than the one along which receptacles 68 and 69 extend.

In the embodiment depicted in FIG. 2, rear guide washer 13 and frontguide washer 14 define a sealed receiving chamber 45 for elastic members25, 26, which is filled with a lubricating agent such as grease.

In order to ensure sealing of receptacle 45, the fastening of rear guidewasher 13 and front guide washer 14 can be implemented by sealedwelding. Specifically, the two guide washers, rear 13 and front 14, arerotationally integral with one another. Guide washers 13 and 14 arecontinuously connected to one another over their entire externalperipheral contour. Other embodiments are possible; for example, guidewashers 13 and 14 can be assembled by bolting using a gasket, or byriveting with or without a gasket.

In an embodiment that is not depicted, a ring constituting a spacercould be inserted between the two guide washers, for example at theirradially outer region, in order to maintain the required axial spacingbetween the guide washers.

In addition, torsional damping device 4 is equipped with sealing means46, 47 (FIG. 12). In the interest of clarity, all elements identical tothose of FIG. 2 are labeled with the same reference numbers. FIG. 12 isa simplified depiction of FIG. 2. These sealing means 46, 47 have anelastically deformable first sealing washer 46 placed between web 15 andrear guide washer 13, ensuring sealing between web 15 and rear guidewasher 13. These sealing means also have a second sealing washer 47placed between front phase washer 33 and front guide washer 14, ensuringsealing between front phase washer 33 and front guide washer 14.

Other sealing means can be provided. In particular, FIG. 13 depicts avariant of the embodiment depicted in FIG. 12, in which the position offront phase washer 33 with respect to front guide washer 14 is depicted.As in FIG. 12, elements identical to the elements described for FIG. 2have the same references in FIG. 13.

Front phase washer 33 forms a first planar portion 72 adjoined against asecond planar portion 73 constituted by front guide washer 14. Theplanar-to-planar adjoining of front phase washer 33 onto front guidewasher 14 allows sealing between those two elements to be ensured. Thisplanar-to-planar adjoining of front phase washer 33 and front guidewasher 14 can be associated, or not, with the presence of second sealingwasher 47.

The device as illustrated in FIG. 13 differs from the device asillustrated in FIG. 12 by the absence of sealing washer 47 between frontguide washer 14 and front phase washer 33.

FIGS. 9 and 10 illustrate another embodiment of the invention in which afront guide washer 130 and a rear guide washer 140 are connected to oneanother by means of at least one connecting spacer 620. Severalconnecting spacers such as 620 can be disposed circumferentially. In theexample illustrated, three connecting spacers such as 620 are provided.

This connecting spacer 620 allows the two guide washers to benon-rotatably connected to one another. This connecting spacer 620 alsoconstitutes a limit stop for the front guide washer 130 and for the rearthe guide washer 140 with respect to an annular front phase washer 320and an annular rear phase washer 340, and with respect to an annular web150. The connecting spacer 620 constitutes a stop that can be referredto as “telescoping,” since upon rotation of the two guide washers 130and 140, the connecting spacer 620 is capable of coming into contactwith the phase washers 320 and 340 and then with the web 150. As bestshown in FIG. 10, each of the front and rear guide washers 130 and 140,the web 150 and the front and rear phase washers 320 and 340 engages allof the elastic members 250 and 260 of the at least one group of elasticmembers 250 and 260.

For this, front phase washer 320, the web 150, and the rear phase washer340, have respective oblong receptacles 630, 640, 650 configured toallow connecting spacer 620 to pass (FIG. 10). Each of the receptacles630, 640, 650 has a continuous perimeter defining circumferentiallyopposite edges. The receptacles 630, 640, 650 are also configured insuch a way that the connecting spacer 620 is capable of coming to a stopagainst any of the circumferentially opposite edges of the receptacle630 of the front phase washer 320 and any of another corresponding edgesof the receptacles 650 of the rear phase washer 340, then comes intoabutment against an edge of the receptacle 640 of the web 150 at a latertime. The connecting spacer 620 is located close to a damper axis X″ ofa torsional damping device 110. Each of the receptacles 630, 640, and650 is preferably oblong in shape.

A pendulum damper (not illustrated) can also be provided and can beconnected to the phase washers 320 and 340 by means of the connectingspacer 620, similar to the connecting spacer 52 as described previously.Or else another connecting spacer, distinct from the one serving as astop, can be provided. This other spacer would then pass through theguide washer 140. The placement of this other connecting spacer isrepresented by an orifice 680 constituted through each of the phasewashers 320 and 340. This orifice 680 is located on the same circle asthe one on which the connecting spacer 620 is located. This orifice 680is located between two tabs 151 and 152 of the web 150. As a variant,the web 150 could have oblong receptacles so as to allow passage of theother connecting spacer and deflection of the phase washers 320 and 340.

In the example as illustrated in FIGS. 9 and 10, the web 150 isnon-rotatable connected to a hub 160 capable of being non-rotatablyconnected to an input shaft of a gearbox. In this example, the web 150is in one piece with the hub 160, but could be constituted by a partdistinct from the hub 160, but integral with (i.e., non-moveablyattached to) the hub 160. A front bearing 170 is disposed between thefront guide washer 130 and the hub 160. A rear bearing 180 is disposedbetween the rear guide washer 140 and the hub 160. The front bearing 170is disposed between the front phase washer 320 and the hub 160. The rearbearing 180 is disposed between the rear phase washer 340 and the samehub 160. The front bearing 170 and the rear bearing 180 are eachL-shaped, having a respective first axial abutment face 171, 181 and arespective second axial abutment face 172, 182. The first abutment faceof the bearings 170 and 180 is capable of receiving a radially inner endrespectively of the front guide washer 130 and of the rear guide washer140. The second abutment face of the bearings 170 and 180 is capable ofreceiving a radially inner end of the front phase washer 320 and of therear phase washer 340.

Front bearing 170 and rear bearing 180 have a respective third radialabutment face 173 and 183, intended to come into abutment against acorresponding face respectively of front guide washer 130 and of rearguide washer 140.

Guide washers 130, 140 can constitute the torque input element inso-called “forward” mode, web 150 then constituting the torque outputelement. Guide washers 130, 140 can likewise constitute the torqueoutput element in so-called “reverse” mode, web 150 then constitutingthe torque input element. Rear guide washer 140 is connected to afriction disk 120.

Guide washers 130, 140 are also connected to one another by at least onefastening means (not depicted). Guide washers 130, 140 have for thatpurpose orifices 131 and 141 for passage of the fastening means. In anexample, the fastening means can be a screw that can be inserted throughpassage orifices 131 and 141. In the example of FIG. 9, passage orifices131 and 141 are located at the radially external periphery of the guidewashers, while receptacles 630, 640, and 650 that receive connectingspacer 620 are intended to be located at the radially inner periphery ofguide washers 130, 140.

FIG. 11 depicts an assemblage comprising an engine flywheel or inertialwheel 75 capable of being connected to the output shaft of the engine, areaction plate 76 mounted rotationally fixedly to inertial wheel 75 bymeans of rivets or screws (not depicted). The assemblage also comprisesa friction disk 78 capable of being gripped between reaction plate 76and a pressure plate 79 in order to allow rotational coupling ofinertial wheel 75 to the gearbox. Reaction plate 76, friction disk 78,and pressure plate 79 are part of a disk-type clutch. Cover 106 isfastened to reaction plate 76 by means of fastening rivet 77.

The assemblage as illustrated in FIG. 11 also has a pendulum damper 80intended to be coupled to the input shaft of the gearbox. Pendulumdamper 80 has a support member 81 and pendulum flyweights 82 mountedmovably on support member 81. Pendulum damper 80 is located betweeninertial wheel 75 and the input shaft of the gearbox. Pendulum damper 80has anti-tilt means 83 that are designed so that support member 81 andinertial wheel 75 interact with one another so as to maintain supportmember 81 axially in position with respect to inertial wheel 75.

Support member 81 has corrugated shapes 84 capable of interacting withinertial wheel 75 in the event of tilting of support member 81.

Corrugated shapes 84 constitute waves that extend at least partlycircumferentially. These shapes and/or inertial wheel 75 can be coveredwith a substance allowing easy slippage, without friction, of theseshapes against inertial wheel 75.

As a variant, these shapes 84 can be replaced at least in part by pegs(not depicted). As a variant, the shapes or the pegs could be carried byinertial wheel 75.

Shapes 84 are located at a distance from rotation axis X′ of saidassemblage in such a way that they are able to come into contact withinertial wheel 75 or with support member 81 in the event of tilting ofsupport member 81, in order to prevent any contact between pendulumflyweights 82 and inertial wheel 75 and/or reaction plate 76. In theexample illustrated in FIG. 11, in the inactive position support member81 is spaced axially away from inertial wheel 75 by a distance d1. Thisdistance is measured along an axis that is parallel to rotation axis X′.To prevent any contact with reaction plate 76, support member 81 isalso, in an inactive position, spaced away by a distance d2 from atorsional damper 85 coupled to friction disk 78. Distance d2 is alsomeasured along an axis parallel to rotation axis X′.

The assemblage also has a torsional damper 85 coupled to friction disk78. Torsional damper 85 comprises a rear guide washer 86 and a frontguide washer 87. Rear guide washer 86 and front guide washer 87 arecoupled to friction disk 78. Torsional damper 85 also has a web 88rotationally coupled to a central hub 89 that constitutes an integralpart with web 88. Central hub 89 is capable of being coupled to theinput shaft of the gearbox.

At least one group of elastic members 90 is mounted between guidewashers 86 and 87 and web 88. These elastic members 90 act againstrotation of inertial wheel 75/reaction plate 76 with respect to web88/hub 89.

Anti-tilt means 83 and the group of elastic members 90 are preferablysituated on the same circumference.

Support member 81 has corrugated shapes capable of interacting withfront guide washer 87 in the event of tilting of said support member 81.As a variant that is not depicted, these corrugated shapes can also bepresent on front guide washer 87.

As previously, elastic members 90 of the group are arranged in series bymeans of a rear phase washer 91 and a front phase washer 92 that aremounted freely rotatably with respect to guide washers 86, 87 and withrespect to web 88, so that the elastic members of each group deform inphase with one another.

Rear phase washer 91 and front phase washer 92 are fixedly connectedtogether.

A rear bearing 93 and a front bearing 94 are disposed on either side ofweb 88. Support member 81 is coupled indirectly to the torque inputshaft of the gearbox by the fact that support member 81 is fastened onfront bearing 94. Each of these bearings 93, 94 is rotationally coupledto hub 89.

Pendulum flyweights 82 preferably are disposed radially outsidetorsional damper 85.

Inertial wheel 75 and reaction plate 76 constitute a receptacle 95 intowhich pendulum flyweights 82 are inserted.

Friction means can be provided, fastened onto inertial wheel 75 or ontothe sheet metal of pendulum support member 84 or onto front guide washer87.

As a variant, FIGS. 14 and 15 illustrate a bearing 17 identical to theone illustrated in FIG. 2 and to the other bearing constituted by twodistinct parts 97 and 98. Each of the distinct parts can constitute aplain bearing or rolling bearing. The identical elements illustrated inFIG. 14 and in FIG. 2 have the same reference numbers. First part 97 isrotationally fixed with respect to hub 16, while second part 98constitutes a cylindrical part mounted adjoiningly on hub 16. First part97 also has an axial protrusion 100 extending toward the front, intendedto serve as an axial abutment face for front phase washer 33. First part97 serves to center front guide washer 14. Second part 98 allowspendulum support member 49′ to be centered. Second part 98 constitutesan axial stop 103, and the radially inner periphery of pendulum support49′ extends axially and has a surface 104 complementary to axial stop103. Axial stop 103 is configured so as to prevent axial displacement ofpendulum support 49′ toward radial portion 101 of hub 16.

FIG. 16 illustrates a damping device having tapered bearing 105 servingas a support for front phase washer 33. FIG. 16 also illustrates anaxial stud 109 carried by web 15 and serving as a stop for rear phasewasher 32 and front phase washer 33. Another bearing 108 is alsodepicted, and serves to support rear guide washer 13. Bearing 98 ispositioned between hub 16 and support member 49.

A transmission assemblage comprising a damping device as described aboveis assembled in the following manner: Front phase washer 32 and rearphase washer 33 are installed on either side of web 15. The elasticmembers are then inserted into windows 71 and 70 respectively of phasewashers 32, 33 and of web 15. Front guide washer 14 is placed againstfront phase washer 33. Rear guide washer 13 is placed against rear phasewasher 32. Connecting member 52 is then inserted through rear guidewasher 13. Pendulum support member 49 is placed onto front guide washer14. Connecting member 52 is then fastened onto pendulum support member49.

More specifically, before the installation of support member 49 on frontguide washer 14, provision is made to fasten friction disk 12 onto rearguide washer 13, and to place reaction plate 8 onto a first face offriction disk 12 situated facing pendulum damper 48. Pressure plate 11is then placed facing a second face of friction disk 12, said secondface being opposite to the first face. The clutch mechanism constitutedby cover 9 and diaphragm 96 is then connected to reaction plate 8.

Subassemblies are firstly constituted separately from one another.Pendulum damper 48 is assembled by mounting pendulum weights on supportmember 49. The clutch mechanism 9, 96 is also assembled. Lastly, rearguide washer 13 and front guide washer 14, rear phase washer 32 andfront phase washer 33, as well as web 15 and springs 25 and 26, areinstalled in order to constitute a subassembly in the form of a hollowdisk, to which friction disk 12 is fastened. The clutch mechanism 9, 96,reaction plate 8, and the disk-shaped subassembly are then assembled.Connecting member 52 is inserted through rear guide washer 13. Pendulumdamper 48 is installed onto front guide washer 14 by riveting connectingmember 52. Hole 107 is then filled using a sealing stopper (notdepicted).

Concurrently, inertial wheel 6 is coupled to the crankshaft of anengine. The subassembly constituted by the clutch mechanism 9, 96,reaction plate 8, pressure plate 11, clutch disk 12, and damping device4 is then mounted on inertial wheel 6.

Although the invention has been described in conjunction with severalspecific embodiments, it is very apparent that it is in no way limitedthereto and that it comprises all technical equivalents of the meansdescribed as well as combinations thereof, if the latter are within theframework of the invention. In particular, a clutch or a torqueconverter can be disposed in the transmission system between the outputof the elastic-member damper and the input shaft of the gearbox.

Use of the verb “have,” “comprise,” or “include,” and of conjugatedforms thereof, does not exclude the presence of elements or steps otherthan those set forth in a claim. Use of the indefinite article “a” or“an” for an element or step does not, unless otherwise indicated,exclude the presence of a plurality of such elements or steps.

In the claims, any reference character in parentheses cannot beinterpreted as a limitation of the claim.

The invention claimed is:
 1. A torsional damping device (110)comprising: a torque input element (130, 140) rotatable around a damperaxis X″; a torque output element (150) rotatable around the damper axisX″; at least one phasing member (320, 340) freely rotatable around thedamper axis X″ relative to both the torque input element and the torqueoutput element; and at least one group of elastic members (250, 260)mounted on the at least one phasing member between the torque inputelement and torque output element, the at least one group of elasticmembers acting against rotation of the torque input element and thetorque output element with respect to one another; elastic members ofthe at least one group of elastic members being arranged in series bythe at least one phasing member (320, 340) so that the elastic membersof the at least one group of elastic members deform in phase with oneanother; the torque input element having at least one stop member (620)limiting rotation of the torque input element relative to the outputelement and relative to the at least one phasing member; the at leastone stop member (620) attached to the torque input element; one of theelastic members of the at least one group of elastic members being incontact with the torque output element (150) only at one end and withthe at least one phasing member (320, 340) only at an opposite end. 2.The torsional damping device according to claim 1, wherein the torqueinput element includes a first guide washer (130) and a second guidewasher (140), wherein the first and second guide washers arenon-rotatably connected to one another by at least one first connectingmember (620), and wherein the at least one first connecting member isthe at least one stop member.
 3. The torsional damping device accordingto claim 2, wherein the torque output element includes a web (150),wherein the first phase washer and the second phase washer being placedon either side of the web, and wherein the at least one stop memberextends between the first guide washer and the second guide washer whiletraversing the first guide washer, the web, and the second guide washer.4. The torsional damping device according to claim 2, wherein the atleast one stop member constitutes a connecting spacer.
 5. The torsionaldamping device according to claim 2, wherein the at least one stopmember traverses the at least one phasing member.
 6. The torsionaldamping device according to claim 2, wherein the at least one stopmember has a cylindrical shape of one of circular, oval and prismaticcross section.
 7. The torsional damping device according to claim 1,wherein the at least one stop member constitutes a connecting spacer. 8.The torsional damping device according to claim 7, wherein the at leastone stop member traverses the at least one phasing member.
 9. Thetorsional damping device according to claim 7, wherein the at least onestop member has a cylindrical shape of one of circular, oval andprismatic cross section.
 10. The torsional damping device according toclaim 1, wherein the at least one stop member traverses the at least onephasing member.
 11. The torsional damping device according to claim 10,wherein the at least one phasing member has at least one oblongreceptacle (630, 650) having a continuous perimeter, and wherein the atleast one stop member traversing the at least one phasing member throughthe at least one oblong receptacle.
 12. The torsional damping deviceaccording to claim 11, wherein the at least one stop member has acylindrical shape of one of circular, oval and prismatic cross section.13. The torsional damping device according to claim 10, wherein the atleast one stop member has a cylindrical shape of one of circular, ovaland prismatic cross section.
 14. The torsional damping device accordingto claim 1, wherein the at least one stop member has a cylindrical shapeof circular, oval, or prismatic cross section.
 15. The torsional dampingdevice according to claim 1, wherein the at least one phasing memberincludes a first phase washer (320) and a second phase washer (340), andwherein the first and second phase washers are non-rotatably connectedto one another by at least one second connecting member and are placedon either side of the torque input element or of the torque outputelement.
 16. The device according to claim 1, in which the phasingmember is constituted by a first phase washer (320) and by a secondphase washer (340), the two phase washers being connected to one anotherby at least one second connecting means (680), the second connectingmeans being located on the same circle as the one on which the stopmeans (620) is disposed.
 17. A component for a transmission system of amotor vehicle, the component being one of a dual mass flywheel, ahydrodynamic torque converter and a friction disk, the componentcomprising the torsional damping device (4) according to claim
 1. 18. Amotor vehicle transmission assemblage intended to be disposed between acombustion engine (1) equipped with a crankshaft and a gearbox (2)equipped with an input shaft, the assemblage comprising: an electricmachine (500) having a stator (501) and a rotor (502) rotationallymovable around an axis X; a clutch (330) arranged to couple or decouplethe crankshaft of the engine and the rotor of the electric machine;torsional damping device (4) according to claim 1, the torsional dampingdevice configured to transmit torque and to dampen rotationalirregularities between the rotor and the input shaft of the gearbox. 19.The torsional damping device according to claim 1, wherein the torsionaldamping device is configured to transmit torque from the torque inputelement to the torque output element solely through the at least onephasing member and the at least one group of elastic members.
 20. Thetorsional damping device according to claim 1, wherein the torque outputelement includes a web (150) and a hub (160) integral with the web (150)and coaxial with the damper axis X″.